Method for determining a preferred engine operation in a hybrid powertrain system during blended braking

ABSTRACT

A hybrid transmission is operative to transfer power between an input member and a torque machine and an output member. A method for controlling the powertrain system during a braking event includes evaluating candidate input torques. An output torque reactable through the transmission to the driveline and limited within the range of permissible output torques is determined for the candidate engine input torque. A preferred input torque is determined.

CROSS REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of U.S. Provisional Application No. 60/985,234, filed on Nov. 4, 2007 which is hereby incorporated herein by reference.

TECHNICAL FIELD

This disclosure pertains to control systems for hybrid powertrain systems.

BACKGROUND

The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.

Known hybrid powertrain architectures can include multiple torque-generative devices, including internal combustion engines and non-combustion torque machines, e.g., electric machines, which transmit torque through a transmission device to an output member. One exemplary hybrid powertrain includes a two-mode, compound-split, electromechanical transmission which utilizes an input member for receiving tractive torque from a prime mover power source, preferably an internal combustion engine, and an output member. The output member can be operatively connected to a driveline for a motor vehicle for transmitting tractive torque thereto. Machines, operative as motors or generators, can generate torque inputs to the transmission independently of a torque input from the internal combustion engine. The machines may transform vehicle kinetic energy transmitted through the vehicle driveline to energy that is storable in an energy storage device. A control system monitors various inputs from the vehicle and the operator and provides operational control of the hybrid powertrain, including controlling transmission operating state and gear shifting, controlling the torque-generative devices, and regulating the power interchange among the energy storage device and the machines to manage outputs of the transmission, including torque and rotational speed.

SUMMARY

A powertrain system includes an engine, a transmission and a torque machine connected to an energy storage device. The transmission is operative to transfer power between the engine and the torque machine. An output member is coupled to a driveline coupled to a wheel including an actuable friction brake. The torque machine is operative to react torque transferred from the wheel through the driveline to the output member of the transmission, the engine selectively operative in an all-cylinder state and a cylinder deactivation state and selectively operative in a fueled state and a fuel cutoff state. A method for controlling the powertrain system includes monitoring operator torque requests, detecting a braking event based upon the operator torque requests, determining a range of permissible output torques based upon the operator torque requests, evaluating candidate input torques from the engine for each of the engine states and determining corresponding candidate output torques reactable through the output member of the transmission to the driveline, the candidate output torques limited within the range of permissible output torques, determining power costs for operating the hybrid transmission for the candidate input torques, and identifying a preferred engine state and a preferred input torque comprising the candidate input torque and the corresponding engine state having a minimum power cost for operating the hybrid transmission during the braking event.

BRIEF DESCRIPTION OF THE DRAWINGS

One or more embodiments will now be described, by way of example, with reference to the accompanying drawings, in which:

FIG. 1 is a schematic diagram of an exemplary hybrid powertrain, in accordance with the present disclosure;

FIG. 2 is a schematic diagram of an exemplary architecture for a control system and hybrid powertrain, in accordance with the present disclosure;

FIGS. 3, 4 and 5 are schematic flow diagrams of a control scheme, in accordance with the present disclosure; and

FIG. 6 is a datagraph, in accordance with the present disclosure.

DETAILED DESCRIPTION

Referring now to the drawings, wherein the showings are for the purpose of illustrating certain exemplary embodiments only and not for the purpose of limiting the same, FIGS. 1 and 2 depict an exemplary hybrid powertrain system. The exemplary hybrid powertrain system in accordance with the present disclosure is depicted in FIG. 1, comprising a two-mode, compound-split, electromechanical hybrid transmission 10 operatively connected to an engine 14 and torque machines comprising first and second electric machines (‘MG-A’) 56 and (‘MG-B’) 72. The engine 14 and first and second electric machines 56 and 72 each generate mechanical power which can be transferred to the transmission 10. The power generated by the engine 14 and the first and second electric machines 56 and 72 and transferred to the transmission 10 is described in terms of input and motor torques, referred to herein as T_(I), T_(A), and T_(B) respectively, and speed, referred to herein as N_(I), N_(A), and N_(B), respectively.

The exemplary engine 14 comprises a multi-cylinder internal combustion engine selectively operative in several states to transfer torque to the transmission 10 via an input shaft 12, and can be either a spark-ignition or a compression-ignition engine. The engine 14 includes a crankshaft (not shown) operatively coupled to the input shaft 12 of the transmission 10. A rotational speed sensor 11 monitors rotational speed of the input shaft 12. Power output from the engine 14, comprising rotational speed and engine torque, can differ from the input speed N, and the input torque T_(I) to the transmission 10 due to placement of torque-consuming components on the input shaft 12 between the engine 14 and the transmission 10, e.g., a hydraulic pump (not shown) and/or a torque management device (not shown).

The exemplary transmission 10 comprises three planetary-gear sets 24, 26 and 28, and four selectively engageable torque-transferring devices, i.e., clutches C1 70, C2 62, C3 73, and C4 75. As used herein, clutches refer to any type of friction torque transfer device including single or compound plate clutches or packs, band clutches, and brakes, for example. A hydraulic control circuit (‘HYD’) 42, preferably controlled by a transmission control module (hereafter ‘TCM’) 17, is operative to control clutch states. Clutches C2 62 and C4 75 preferably comprise hydraulically-applied rotating friction clutches. Clutches C1 70 and C3 73 preferably comprise hydraulically-controlled stationary devices that can be selectively grounded to a transmission case 68. Each of the clutches C1 70, C2 62, C3 73, and C4 75 is preferably hydraulically applied, selectively receiving pressurized hydraulic fluid via the hydraulic control circuit 42.

The first and second electric machines 56 and 72 preferably comprise three-phase AC machines, each including a stator (not shown) and a rotor (not shown), and respective resolvers 80 and 82. The motor stator for each machine is grounded to an outer portion of the transmission case 68, and includes a stator core with coiled electrical windings extending therefrom. The rotor for the first electric machine 56 is supported on a hub plate gear that is operatively attached to shaft 60 via the second planetary gear set 26. The rotor for the second electric machine 72 is fixedly attached to a sleeve shaft hub 66.

Each of the resolvers 80 and 82 preferably comprises a variable reluctance device including a resolver stator (not shown) and a resolver rotor (not shown). The resolvers 80 and 82 are appropriately positioned and assembled on respective ones of the first and second electric machines 56 and 72. Stators of respective ones of the resolvers 80 and 82 are operatively connected to one of the stators for the first and second electric machines 56 and 72. The resolver rotors are operatively connected to the rotor for the corresponding first and second electric machines 56 and 72. Each of the resolvers 80 and 82 is signally and operatively connected to a transmission power inverter control module (hereafter ‘TPIM’) 19, and each senses and monitors rotational position of the resolver rotor relative to the resolver stator, thus monitoring rotational position of respective ones of first and second electric machines 56 and 72. Additionally, the signals output from the resolvers 80 and 82 are interpreted to provide the rotational speeds for first and second electric machines 56 and 72, i.e., N_(A) and N_(B), respectively.

The transmission 10 includes an output member 64, e.g. a shaft, which is operably connected to a driveline 90 for a vehicle (not shown), to provide output power to the driveline 90 that is transferred to vehicle wheels 93, one of which is shown in FIG. 1. The output power at the output member 64 is characterized in terms of an output rotational speed N_(O) and an output torque T_(O). A transmission output speed sensor 84 monitors rotational speed and rotational direction of the output member 64. Each of the vehicle wheels 93 is preferably equipped with a friction brake 94 and a sensor (not shown) adapted to monitor wheel speed, the output of which is monitored by a control module of a distributed control module system described with respect to FIG. 2, to determine vehicle speed, and absolute and relative wheel speeds for braking control, traction control, and vehicle acceleration management.

The input torque from the engine 14 and the motor torques from the first and second electric machines 56 and 72 (T_(I), T_(A), and T_(B) respectively) are generated as a result of energy conversion from fuel or electrical potential stored in an electrical energy storage device (hereafter ‘ESD’) 74. The ESD 74 is high voltage DC-coupled to the TPIM 19 via DC transfer conductors 27. The transfer conductors 27 include a contactor switch 38. When the contactor switch 38 is closed, under normal operation, electric current can flow between the ESD 74 and the TPIM 19. When the contactor switch 38 is opened electric current flow between the ESD 74 and the TPIM 19 is interrupted. The TPIM 19 transmits electrical power to and from the first electric machine 56 by transfer conductors 29, and the TPIM 19 similarly transmits electrical power to and from the second electric machine 72 by transfer conductors 31 to meet the torque commands for the first and second electric machines 56 and 72 in response to the motor torque commands T_(A) and T_(B). Electrical current is transmitted to and from the ESD 74 in accordance with whether the ESD 74 is being charged or discharged.

The TPIM 19 includes the pair of power inverters (not shown) and respective motor control modules (not shown) configured to receive the torque commands and control inverter states therefrom for providing motor drive or regeneration functionality to meet the commanded motor torques T_(A) and T_(B). The power inverters comprise known complementary three-phase power electronics devices, and each includes a plurality of insulated gate bipolar transistors (not shown) for converting DC power from the ESD 74 to AC power for powering respective ones of the first and second electric machines 56 and 72, by switching at high frequencies. The insulated gate bipolar transistors form a switch mode power supply configured to receive control commands. There is typically one pair of insulated gate bipolar transistors for each phase of each of the three-phase electric machines. States of the insulated gate bipolar transistors are controlled to provide motor drive mechanical power generation or electric power regeneration functionality. The three-phase inverters receive or supply DC electric power via DC transfer conductors 27 and transform it to or from three-phase AC power, which is conducted to or from the first and second electric machines 56 and 72 for operation as motors or generators via transfer conductors 29 and 31 respectively.

FIG. 2 is a schematic block diagram of the distributed control module system. The elements described hereinafter comprise a subset of an overall vehicle control architecture, and provide coordinated system control of the exemplary hybrid powertrain described in FIG. 1. The distributed control module system synthesizes pertinent information and inputs, and executes algorithms to control various actuators to meet control objectives, including objectives related to fuel economy, emissions, performance, drivability, and protection of hardware, including batteries of ESD 74 and the first and second electric machines 56 and 72. The distributed control module system includes an engine control module (hereafter ‘ECM’) 23, the TCM 17, a battery pack control module (hereafter ‘BPCM’) 21, and the TPIM 19. A hybrid control module (hereafter ‘HCP’) 5 provides supervisory control and coordination of the ECM 23, the TCM 17, the BPCM 21, and the TPIM 19. A user interface (‘UI’) 13 is operatively connected to a plurality of devices through which a vehicle operator controls or directs operation of the electromechanical hybrid powertrain. The devices include an accelerator pedal 113 (‘AP’), an operator brake pedal 112 (‘BP’), a transmission gear selector 114 (‘PRNDL’), and a vehicle speed cruise control (not shown). The transmission gear selector 114 may have a discrete number of operator-selectable positions, including the rotational direction of the output member 64 to enable one of a forward and a reverse direction.

The aforementioned control modules communicate with other control modules, sensors, and actuators via a local area network (hereafter ‘LAN’) bus 6. The LAN bus 6 allows for structured communication of states of operating parameters and actuator command signals between the various control modules. The specific communication protocol utilized is application-specific. The LAN bus 6 and appropriate protocols provide for robust messaging and multi-control module interfacing between the aforementioned control modules, and other control modules providing functionality including e.g., antilock braking, traction control, and vehicle stability. Multiple communications buses may be used to improve communications speed and provide some level of signal redundancy and integrity. Communication between individual control modules can also be effected using a direct link, e.g., a serial peripheral interface (‘SPI’) bus (not shown).

The HCP 5 provides supervisory control of the hybrid powertrain, serving to coordinate operation of the ECM 23, TCM 17, TPIM 19, and BPCM 21. Based upon various input signals from the user interface 13 and the hybrid powertrain, including the ESD 74, the HCP 5 determines an operator torque request, an output torque command, an engine input torque command, clutch torque(s) for the applied torque-transfer clutches C1 70, C2 62, C3 73, C4 75 of the transmission 10, and the motor torque commands T_(A) and T_(B) for the first and second electric machines 56 and 72.

The ECM 23 is operatively connected to the engine 14, and functions to acquire data from sensors and control actuators of the engine 14 over a plurality of discrete lines, shown for simplicity as an aggregate bi-directional interface cable 35. The ECM 23 receives the engine input torque command from the HCP 5. The ECM 23 determines the actual engine input torque, T_(I), provided to the transmission 10 at that point in time based upon monitored engine speed and load, which is communicated to the HCP 5. The ECM 23 monitors input from the rotational speed sensor 11 to determine the engine input speed to the input shaft 12, which translates to the transmission input speed, N_(I). The ECM 23 monitors inputs from sensors (not shown) to determine states of other engine operating parameters including, e.g., a manifold pressure, engine coolant temperature, ambient air temperature, and ambient pressure. The engine load can be determined, for example, from the manifold pressure, or alternatively, from monitoring operator input to the accelerator pedal 113. The ECM 23 generates and communicates command signals to control engine actuators, including, e.g., fuel injectors, ignition modules, and throttle control modules, none of which are shown.

The TCM 17 is operatively connected to the transmission 10 and monitors inputs from sensors (not shown) to determine states of transmission operating parameters. The TCM 17 generates and communicates command signals to control the transmission 10, including controlling the hydraulic control circuit 42. Inputs from the TCM 17 to the HCP 5 include estimated clutch torques for each of the clutches, i.e., C1 70, C2 62, C3 73, and C4 75, and rotational output speed, NO, of the output member 64. Other actuators and sensors may be used to provide additional information from the TCM 17 to the HCP 5 for control purposes. The TCM 17 monitors inputs from pressure switches (not shown) and selectively actuates pressure control solenoids (not shown) and shift solenoids (not shown) of the hydraulic control circuit 42 to selectively actuate the various clutches C1 70, C2 62, C3 73, and C4 75 to achieve various transmission operating range states, as described hereinbelow.

The BPCM 21 is signally connected to sensors (not shown) to monitor the ESD 74, including states of electrical current and voltage parameters, to provide information indicative of parametric states of the batteries of the ESD 74 to the HCP 5. The parametric states of the batteries preferably include battery state-of-charge, battery voltage, battery temperature, and available battery power, referred to as a range P_(BAT) _(—) _(MIN) to P_(BAT) _(—) _(MAX).

A brake control module (hereafter ‘BrCM’) 22 is operatively connected to the friction brakes 94 on each of the vehicle wheels 93. The BrCM 22 monitors the operator input to the brake pedal 112 and generates control signals to control the friction brakes 94 and sends a control signal to the HCP 5 to operate the first and second electric machines 56 and 72 based thereon, to effect vehicle braking through a process referred to as blended braking.

Each of the control modules ECM 23, TCM 17, TPIM 19, BPCM 21, and BrCM 22 is preferably a general-purpose digital computer comprising a microprocessor or central processing unit, storage mediums comprising read only memory (‘ROM’), random access memory (‘RAM’), electrically programmable read only memory (‘EPROM’), a high speed clock, analog to digital (‘A/D’) and digital to analog (‘D/A’) circuitry, and input/output circuitry and devices (‘I/O’) and appropriate signal conditioning and buffer circuitry. Each of the control modules has a set of control algorithms, comprising resident program instructions and calibrations stored in one of the storage mediums and executed to provide the respective functions of each computer. Information transfer between the control modules is preferably accomplished using the LAN bus 6 and SPI buses. The control algorithms are executed during preset loop cycles such that each algorithm is executed at least once each loop cycle. Algorithms stored in the non-volatile memory devices are executed by one of the central processing units to monitor inputs from the sensing devices and execute control and diagnostic routines to control operation of the actuators, using preset calibrations. Loop cycles are executed at regular intervals, for example each 3.125, 6.25, 12.5, 25 and 100 milliseconds during ongoing operation of the hybrid powertrain. Alternatively, algorithms may be executed in response to the occurrence of an event.

The exemplary hybrid powertrain selectively operates in one of several states that can be described in terms of engine states comprising one of an engine-on state (‘ON’) and an engine-off state (‘OFF’), and transmission operating range states comprising a plurality of fixed gears and continuously variable operating modes, described with reference to Table 1, below.

TABLE 1 Engine Transmission Operating Applied Description State Range State Clutches M1_Eng_Off OFF EVT Mode 1 C1 70 M1_Eng_On ON EVT Mode 1 C1 70 G1 ON Fixed Gear Ratio 1 C1 70 C4 75 G2 ON Fixed Gear Ratio 2 C1 70 C2 62 M2_Eng_Off OFF EVT Mode 2 C2 62 M2_Eng_On ON EVT Mode 2 C2 62 G3 ON Fixed Gear Ratio 3 C2 62 C4 75 G4 ON Fixed Gear Ratio 4 C2 62 C3 73

Each of the transmission operating range states is described in the table and indicates which of the specific clutches C1 70, C2 62, C3 73, and C4 75 are applied for each of the operating range states. A first continuously variable mode, i.e., EVT Mode 1, or M1, is selected by applying clutch C1 70 only in order to “ground” the outer gear member of the third planetary gear set 28. The engine state can be one of ON (‘M1_Eng_On’) or OFF (‘M1_Eng_Off’). A second continuously variable mode, i.e., EVT Mode 2, or M2, is selected by applying clutch C2 62 only to connect the shaft 60 to the carrier of the third planetary gear set 28. The engine state can be one of ON (‘M2_Eng_On’) or OFF (‘M2_Eng_Off’). For purposes of this description, when the engine state is OFF, the engine input speed is equal to zero revolutions per minute (‘RPM’), i.e., the engine crankshaft is not rotating. A fixed gear operation provides a fixed ratio operation of input-to-output speed of the transmission 10, i.e., N_(I)/N_(O). A first fixed gear operation (‘G1’) is selected by applying clutches C1 70 and C4 75. A second fixed gear operation (‘G2’) is selected by applying clutches C1 70 and C2 62. A third fixed gear operation (‘G3’) is selected by applying clutches C2 62 and C4 75. A fourth fixed gear operation (‘G4’) is selected by applying clutches C2 62 and C3 73. The fixed ratio operation of input-to-output speed increases with increased fixed gear operation due to decreased gear ratios in the planetary gears 24, 26, and 28. The rotational speeds of the first and second electric machines 56 and 72, N_(A) and N_(B) respectively, are dependent on internal rotation of the mechanism as defined by the clutching and are proportional to the input speed measured at the input shaft 12.

In response to operator input via the accelerator pedal 113 and brake pedal 112 as captured by the user interface 13, the HCP 5 and one or more of the other control modules determine torque commands to control the torque generative devices comprising the engine 14 and the first and second electric machines 56 and 72 to meet the operator torque request at the output member 64 and transferred to the driveline 90. Based upon input signals from the user interface 13 and the hybrid powertrain including the ESD 74, the HCP 5 determines the operator torque request, a commanded output torque from the transmission 10 to the driveline 90, an input torque from the engine 14, clutch torques for the torque-transfer clutches C1 70, C2 62, C3 73, C4 75 of the transmission 10; and the motor torques for the first and second electric machines 56 and 72, respectively, as is described hereinbelow.

Final vehicle acceleration can be affected by other factors including, e.g., road load, road grade, and vehicle mass. The engine state and the transmission operating range state are determined based upon a variety of operating characteristics of the hybrid powertrain. This includes the operator torque request communicated through the accelerator pedal 113 and brake pedal 112 to the user interface 13 as previously described. The transmission operating range state and the engine state may be predicated on a hybrid powertrain torque demand caused by a command to operate the first and second electric machines 56 and 72 in an electrical energy generating mode or in a torque generating mode. The transmission operating range state and the engine state can be determined by an optimization algorithm or routine which determines optimum system efficiency based upon operator demand for power, battery state of charge, and energy efficiencies of the engine 14 and the first and second electric machines 56 and 72. The control system manages torque inputs from the engine 14 and the first and second electric machines 56 and 72 based upon an outcome of the executed optimization routine, and system efficiencies are optimized thereby, to manage fuel economy and battery charging. Furthermore, operation can be determined based upon a fault in a component or system. The HCP 5 monitors the torque-generative devices, and determines the power output from the transmission 10 at output member 64 that is required to meet the operator torque request while meeting other powertrain operating demands, e.g., charging the ESD 74. As should be apparent from the description above, the ESD 74 and the first and second electric machines 56 and 72 are electrically-operatively coupled for power flow therebetween. Furthermore, the engine 14, the first and second electric machines 56 and 72, and the electromechanical transmission 10 are mechanically-operatively coupled to transfer power therebetween to generate a power flow to the output member 64.

FIG. 3 shows a control system architecture for controlling and managing signal flow in a hybrid powertrain system having multiple torque generative devices, described hereinbelow with reference to the hybrid powertrain system of FIGS. 1 and 2, and residing in the aforementioned control modules in the form of executable algorithms and calibrations. The control system architecture is applicable to alternative hybrid powertrain systems having multiple torque generative devices, including, e.g., a hybrid powertrain system having an engine and a single electric machine, a hybrid powertrain system having an engine and multiple electric machines. Alternatively, the hybrid powertrain system can utilize non-electric torque-generative machines and energy storage systems, e.g., hydraulic-mechanical hybrid transmissions (not shown).

In operation, the operator inputs to the accelerator pedal 113 and the brake pedal 112 are monitored to determine the operator torque request. The operator inputs to the accelerator pedal 113 and the brake pedal 112 comprise individually determinable operator torque request inputs including an immediate accelerator output torque request (‘Output Torque Request Accel Immed’), a predicted accelerator output torque request (‘Output Torque Request Accel Prdtd’), an immediate brake output torque request (‘Output Torque Request Brake Immed’), a predicted brake output torque request (‘Output Torque Request Brake Prdtd’) and an axle torque response type (‘Axle Torque Response Type’). As used herein, the term ‘accelerator’ refers to an operator request for forward propulsion preferably resulting in increasing vehicle speed over the present vehicle speed, when the operator selected position of the transmission gear selector 114 commands operation of the vehicle in the forward direction. The terms ‘deceleration’ and ‘brake’ refer to an operator request preferably resulting in decreasing vehicle speed from the present vehicle speed. The immediate accelerator output torque request, the predicted accelerator output torque request, the immediate brake output torque request, the predicted brake output torque request, and the axle torque response type are individual inputs to the control system. Additionally, operation of the engine 14 and the transmission 10 are monitored to determine the input speed (‘Ni’) and the output speed (‘No’).

The immediate accelerator output torque request comprises an immediate torque request determined based upon the operator input to the accelerator pedal 113. The control system controls the output torque from the hybrid powertrain system in response to the immediate accelerator output torque request to cause positive acceleration of the vehicle. The immediate brake output torque request comprises an immediate braking request determined based upon the operator input to the brake pedal 112. The control system controls the output torque from the hybrid powertrain system in response to the immediate brake output torque request to cause deceleration, or negative acceleration, of the vehicle. Vehicle deceleration effected by control of the output torque from the hybrid powertrain system is combined with vehicle deceleration effected by a vehicle braking system (not shown) to decelerate the vehicle to achieve the immediate braking request.

The immediate accelerator output torque request is determined based upon a presently occurring operator input to the accelerator pedal 113, and comprises a request to generate an immediate output torque at the output member 64 preferably to accelerate the vehicle. The immediate accelerator output torque request is unshaped, but can be shaped by events that affect vehicle operation outside the powertrain control. Such events include vehicle level interruptions in the powertrain control for antilock braking, traction control and vehicle stability control, which can be used to unshape or rate-limit the immediate accelerator output torque request.

The predicted accelerator output torque request is determined based upon the operator input to the accelerator pedal 113 and comprises an optimum or preferred output torque at the output member 64. The predicted accelerator output torque request is preferably equal to the immediate accelerator output torque request during normal operating conditions, e.g., when any one of antilock braking, traction control, or vehicle stability is not being commanded. When any one of antilock braking, traction control or vehicle stability is being commanded the predicted accelerator output torque request remains the preferred output torque with the immediate accelerator output torque request being decreased in response to output torque commands related to the antilock braking, traction control, or vehicle stability control.

The immediate brake output torque request is determined based upon the operator input to the brake pedal 112 and the control signal to control the friction brakes 94 to generate friction braking torque.

The predicted brake output torque request comprises an optimum or preferred brake output torque at the output member 64 in response to an operator input to the brake pedal 112 subject to a maximum brake output torque generated at the output member 64 allowable regardless of the operator input to the brake pedal 112. In one embodiment the maximum brake output torque generated at the output member 64 is limited to −0.2 g. The predicted brake output torque request can be phased out to zero when vehicle speed approaches zero regardless of the operator input to the brake pedal 112. As desired by a user, there can be operating conditions under which the predicted brake output torque request is set to zero, e.g., when the operator setting to the transmission gear selector 114 is set to a reverse gear, and when a transfer case (not shown) is set to a four-wheel drive low range. The operating conditions whereat the predicted brake output torque request is set to zero are those in which blended braking is not preferred due to vehicle operating factors.

The axle torque response type comprises an input state for shaping and rate-limiting the output torque response through the first and second electric machines 56 and 72. The input state for the axle torque response type can be an active state, preferably comprising one of a pleasability limited state a maximum range state, and an inactive state. When the commanded axle torque response type is the active state, the output torque command is the immediate output torque. Preferably the torque response for this response type is as fast as possible.

Blended braking includes generating friction braking torque at the wheels 93 and generating output torque at the output member 64 to react with the driveline 90 to decelerate the vehicle in response to the operator input to the brake pedal 112. The BrCM 22 commands the friction brakes 94 to apply braking torque and generates a command for the transmission 10 to create a negative output torque which reacts with the driveline 90 in response to the immediate braking request. Preferably the applied braking torque and the negative output torque can decelerate and stop the vehicle so long as they are sufficient to overcome vehicle kinetic power at wheel(s) 93. The negative output torque reacts with the driveline 90, thus transferring torque to the electromechanical transmission 10 and the engine 14. The negative output torque reacted through the electromechanical transmission 10 can be transferred to one or both of the first and second electric machines 56 and 72 to generate electric power for storage in the ESD 74.

A strategic optimization control scheme (‘Strategic Control’) 310 etermines a preferred input speed (‘Ni_Des’) and a preferred engine state and transmission operating range state (‘Hybrid Range State Des’) based upon the output speed and the operator torque request and based upon other operating parameters of the hybrid powertrain, including battery power limits and response limits of the engine 14, the transmission 10, and the first and second electric machines 56 and 72. The predicted accelerator output torque request and the predicted brake output torque request are input to the strategic optimization control scheme 310. The strategic optimization control scheme 310 is preferably executed by the HCP 5 during each 100 ms loop cycle and each 25 ms loop cycle. The desired operating range state for the transmission 10 and the desired input speed from the engine 14 to the transmission 10 are inputs to the shift execution and engine start/stop control scheme 320.

The shift execution and engine start/stop control scheme 320 commands changes in the transmission operation (‘Transmission Commands’) including changing the operating range state based upon the inputs and operation of the powertrain system. This includes commanding execution of a change in the transmission operating range state if the preferred operating range state is different from the present operating range state by commanding changes in application of one or more of the clutches C1 70, C2 62, C3 73, and C4 75 and other transmission commands. The present operating range state (‘Hybrid Range State Actual’) and an input speed profile (‘Ni_Prof’) can be determined. The input speed profile is an estimate of an upcoming input speed and preferably comprises a scalar parametric value that is a targeted input speed for the forthcoming loop cycle. The engine operating commands and the operator torque request are based upon the input speed profile during a transition in the operating range state of the transmission.

A tactical control scheme (‘Tactical Control and Operation’) 330 is repeatedly executed during one of the control loop cycles to determine engine commands (‘Engine Commands’) for operating the engine 14, including a preferred input torque from the engine 14 to the transmission 10 based upon the output speed, the input speed, and the operator torque request comprising the immediate accelerator output torque request, the predicted accelerator output torque request, the immediate brake output torque request, the predicted brake output torque request, the axle torque response type, and the present operating range state for the transmission. The engine commands also include engine states including one of an all-cylinder operating state and a cylinder deactivation operating state wherein a portion of the engine cylinders are deactivated and unfueled, and engine states including one of a fueled state and a fuel cutoff state. An engine command comprising the preferred input torque of the engine 14 and a present input torque (‘Ti’) reacting between the engine 14 and the input member 12 are preferably determined in the ECM 23. Clutch torques (‘Tcl’) for each of the clutches C1 70, C2 62, C3 73, and C4 75, including the presently applied clutches and the non-applied clutches are estimated, preferably in the TCM 17.

An output and motor torque determination scheme (‘Output and Motor Torque Determination’) 340 is executed to determine the preferred output torque from the powertrain (‘To_cmd’). This includes determining motor torque commands (‘T_(A)’, ‘T_(B)’) to transfer a net commanded output torque to the output member 64 of the transmission 10 that meets the operator torque request, by controlling the first and second electric machines 56 and 72 in this embodiment. The immediate accelerator output torque request, the immediate brake output torque request, the present input torque from the engine 14 and the estimated applied clutch torque(s), the present operating range state of the transmission 10, the input speed, the input speed profile, and the axle torque response type are inputs. The output and motor torque determination scheme 340 executes to determine the motor torque commands during each iteration of one of the loop cycles. The output and motor torque determination scheme 340 includes algorithmic code which is regularly executed during the 6.25 ms and 12.5 ms loop cycles to determine the preferred motor torque commands.

The hybrid powertrain is controlled to transfer the output torque to the output member 64 to react with the driveline 90 to generate tractive torque at wheel(s) 93 to forwardly propel the vehicle in response to the operator input to the accelerator pedal 113 when the operator selected position of the transmission gear selector 114 commands operation of the vehicle in the forward direction. Similarly, the hybrid powertrain is controlled to transfer the output torque to the output member 64 to react with the driveline 90 to generate tractive torque at wheel(s) 93 to propel the vehicle in a reverse direction in response to the operator input to the accelerator pedal 113 when the operator selected position of the transmission gear selector 114 commands operation of the vehicle in the reverse direction. Preferably, propelling the vehicle results in vehicle acceleration so long as the output torque is sufficient to overcome external loads on the vehicle, e.g., due to road grade, aerodynamic loads, and other loads.

FIG. 4 details signal flow in the tactical control scheme (‘Tactical Control and Operation’) 330 for controlling operation of the engine 14, described with reference to the hybrid powertrain system of FIGS. 1 and 2 and the control system architecture of FIGS. 3 and 4. The tactical control scheme 330 includes a tactical optimization control path 350 and a system constraints control path 360 which are preferably executed concurrently. The outputs of the tactical optimization control path 350 are input to an engine state control scheme 370. The outputs of the engine state control scheme 370 and the system constraints control path 360 are input to an engine response type determination scheme (‘Engine Response Type Determination’) 380 for controlling the engine state, the immediate engine torque request, the predicted engine torque request, and the engine response type.

The input from the engine 14 can be described in terms of an engine operating point including engine speed and engine torque which can be converted into the input speed and input torque which react with the input member from the transmission 10. When the engine 14 comprises a spark-ignition engine, a change in the engine operating point can be effected by changing mass of intake air to the engine 14, by controlling position of an engine throttle (not shown) utilizing an electronic throttle control system (not shown), including opening the engine throttle to increase engine torque and closing the engine throttle to decrease engine torque. Changes in the engine operating point can be effected by adjusting ignition timing, including retarding spark timing from a mean-best-torque spark timing to decrease engine torque. When the engine 14 comprises a compression-ignition engine, the engine operating point is controlled by controlling the mass of injected fuel and adjusted by retarding injection timing from a mean-best-torque injection timing to decrease the engine torque. The engine operating point can also be changed to effect a change in the input torque by controlling the engine state between the all-cylinder state and the cylinder deactivation state, and, by controlling the engine state between the engine-fueled state and the fuel cutoff state wherein the engine is rotating and unfueled.

The tactical optimization control path 350 acts on substantially steady-state inputs to select a preferred engine state and to determine a preferred input torque from the engine 14 to the transmission 10. The tactical optimization control path 350 includes an optimization scheme (‘Tactical Optimization’) 354 to determine preferred input torques for operating the engine 14 in the all-cylinder state (‘Input Torque Full’), in the cylinder deactivation state (‘Input Torque Deac’), the all-cylinder state with fuel cutoff (‘Input Torque Full FCO’), and in the cylinder deactivation state with fuel cutoff (‘Input Torque Deac FCO’), and a preferred engine state (‘Preferred Engine State’). Inputs to the optimization scheme 354 include a lead operating range state of the transmission 10 (‘Lead Hybrid Range State’) a lead predicted input acceleration profile (‘Lead Input Acceleration Profile Predicted’) and a predicted range of clutch reactive torques (‘Predicted Clutch Reactive Torque Min/Max’) across each applied clutch in the lead operating range state, which are preferably generated in the shift execution and engine start/stop control scheme 320. Further inputs include predicted electric power limits (‘Predicted Battery Power Limits’), a predicted accelerator output torque request (‘Output Torque Request Accel Prdtd’) and a predicted brake output torque request (‘Output Torque Request Brake Prdtd’). The predicted output torque request for acceleration is shaped through a predicted output torque shaping filter 352 while considering the axle torque response type to yield a predicted accelerator output torque (‘To Accel Prdtd’) and combined with the predicted output torque request for braking to determine the net predicted output torque (‘To Net Prdtd’), which are inputs to the optimization scheme 354. The lead operating range state of the transmission 10 comprises a time-shifted lead of the operating range state of the transmission 10 to accommodate a response time lag between a commanded change in the operating range state and the actual operating range state. Thus the lead operating range state of the transmission 10 is the commanded operating range state. The lead predicted input acceleration profile comprises a time-shifted lead of the predicted input acceleration profile of the input member 12 to accommodate a response time lag between a commanded change in the predicted input acceleration profile and a measured change in the predicted input acceleration profile. Thus the lead predicted input acceleration profile is the predicted input acceleration profile of the input member 12 occurring after the time shift. The parameters designated as ‘lead’ are used to accommodate concurrent transfer of torque through the powertrain converging at the common output member 64 using devices having varying response times. Specifically, the engine 14 can have a response time of an order of magnitude of 300-600 ms, and each of the torque transfer clutches C1 70, C2 62, C3 73, and C4 75 can have response times of an order of magnitude of 150-300 ms, and the first and second electric machines 56 and 72 can have response time of an order of magnitude of 10 ms.

The optimization scheme 354 determines costs for operating the engine 14 in the engine states, which comprise operating the engine fueled and in the all-cylinder state (‘P_(COST FULL FUEL)’), operating the engine unfueled and in the all-cylinder state (‘P_(COST FULL FCO)’), operating the engine fueled and in cylinder deactivation state (‘P_(COST DEAC FUEL)’), and operating the engine unfueled and in the cylinder deactivation state (‘P_(COST DEAC FCO)’). The aforementioned costs for operating the engine 14 are input to a stabilization analysis scheme (‘Stabilization and Arbitration’) 356 along with the actual engine state (‘Actual Engine State’) and allowable or permissible engine state(s) (‘Engine State Allowed’) to select one of the engine states as the preferred engine state (‘Preferred Engine State’).

The preferred input torques for operating the engine 14 in the all-cylinder state and in the cylinder deactivation state with and without fuel cutoff are input to an engine torque conversion calculator 355 and converted to preferred engine torques in the all-cylinder state and in the cylinder deactivation state (‘Engine Torque Full’ and ‘Engine Torque Deac’) and with fuel cutoff in the all-cylinder state and in the cylinder deactivation state (‘Engine Torque Full FCO’ and ‘Engine Torque Deac FCO’) respectively, by taking into account torque-consuming components, e.g., a hydraulic pump, between the engine 14 and the transmission 10. The preferred engine torques and the preferred engine state comprise inputs to the engine state control scheme 370.

The costs for operating the engine 14 include operating costs which are determined based upon factors that include vehicle driveability, fuel economy, emissions, and battery usage. Costs are assigned and associated with fuel and electrical power consumption and are associated with specific operating conditions of the hybrid powertrain. Lower operating costs can be associated with lower fuel consumption at high conversion efficiencies, lower battery power usage and lower emissions and take into account the present operating state of the engine 14.

The preferred engine state and the preferred engine torques in the all-cylinder state and in the cylinder deactivation state are input to the engine state control scheme 370, which includes an engine state machine (‘Engine State Machine’) 372. The engine state machine 372 determines a target engine torque (‘Target Engine Torque’) and an engine state (‘Target Engine State’) based upon the preferred engine torques and the preferred engine state. The target engine torque and the engine state are input to a transition filter 374 which filters the target engine torque to provide a filtered target engine torque (‘Filtered Target Engine Torque’) and which enables transitions between engine states. The engine state machine 372 outputs a command that indicates selection of one of the cylinder deactivation state and the all-cylinder state (‘DEAC Selected’) and indicates selection of one of the engine-fueled state and the deceleration fuel cutoff state (‘FCO Selected’).

The selection of one of the cylinder deactivation state and the all-cylinder state and the selection of one of the engine-fueled state and the deceleration fuel cutoff state, the filtered target engine torque, and the minimum and maximum engine torques are input to the engine response type determination scheme 380.

The system constraints control path 360 determines the constraints on the input torque, comprising minimum and maximum input torques (‘Input Torque Hybrid Minimum’ and ‘Input Torque Hybrid Maximum’) that can be reacted by the transmission 10. The minimum and maximum input torques are determined based upon constraints to the transmission 10, the first and second electric machines 56 and 72, and the ESD 74, which affect the capacity of the transmission 10 and the electric machines 56 and 72.

Inputs to the system constraints control path 360 include the immediate output torque request as measured by the accelerator pedal 113 combined with the torque intervention control (‘Output Torque Request Accel Immed’) and the immediate output torque request as measured by the brake pedal 112 combined with the torque intervention control (‘Output Torque Request Brake Immed’). The immediate output torque request is shaped through an immediate output torque shaping filter 362 while considering the axle torque response type to yield an immediate accelerator output torque (‘To Accel Immed’) and is combined with the immediate output torque request for braking to determine the net immediate output torque (‘To Net Immed’). The net immediate output torque and the immediate accelerator output torque are inputs to a constraints scheme (‘Output and Input Torque Constraints’) 364. Other inputs to the constraints scheme 364 include the lead operating range state of the transmission 10, an immediate lead input acceleration profile (‘Lead Input Acceleration Profile Immed’), a lead immediate clutch reactive torque range (‘Lead Immediate Clutch Reactive Torque Min/Max’) for each applied clutch in the lead operating range state, and the tactical control electric power constraints (‘Tactical Control Electric Power Constraints’) comprising the range from the minimum tactical control electric power constraint P_(BAT) _(—) _(MIN) _(—) _(TC) to the maximum tactical control electric power constraint P_(BAT) _(—) _(MAX) _(—) _(TC). The tactical control electric power constraints are outputted from a battery power function (‘Battery Power Control’) 366. A targeted lead input acceleration profile comprises a time-shifted lead of the immediate input acceleration profile of the input member 12 to accommodate a response time lag between a commanded change in the immediate input acceleration profile and a measured change in the immediate input acceleration profile. The lead immediate clutch reactive torque range comprises a time-shifted lead of the immediate clutch reactive torque range of the clutches to accommodate a response time lag between a commanded change in the immediate clutch torque range and a measured change in the immediate clutch reactive torque range. The constraints scheme 364 determines an output torque range for the transmission 10, and then determines the minimum and maximum input torques that can be reacted by the transmission 10 based upon the aforementioned inputs.

The minimum and maximum input torques are input to the engine torque conversion calculator 355 and converted to minimum and maximum engine torques (‘Engine Torque Hybrid Minimum’ and ‘Engine Torque Hybrid Maximum’ respectively), by taking into account torque-consuming components, e.g., a hydraulic pump, parasitic and other loads introduced between the engine 14 and the transmission 10.

The filtered target engine torque, the output of the engine state machine 372 and the minimum and maximum engine torques are input to the engine response type determination scheme 380. The engine response type determination scheme 380 limits the filtered target engine torque to the minimum and maximum hybrid engine torques and outputs the engine commands to the ECM 23 for controlling the engine torques to an immediate engine torque request (‘Engine Torque Request Immed’) and a predicted engine torque request (‘Engine Torque Request Prdtd’). Other commands control the engine state to one of the engine fueled state and the fuel cutoff state (‘FCO Request’) and to one of the cylinder deactivation state and the all-cylinder state (‘DEAC Request’). Another output comprises an engine response type (‘Engine Response Type’). When the filtered target engine torque is within the range between the minimum and maximum engine torques, the engine response type is inactive. When the filtered target engine torque drops below the maximum constraint of the engine torque (‘Engine Torque Hybrid Maximum’) the engine response type is active, indicating a need for an immediate change in the engine torque, e.g., through engine spark control to change the engine torque to fall within the constraints of the minimum and maximum engine torques.

FIG. 5 shows details of the tactical optimization scheme 354 of the tactical optimization control path 350. The tactical optimization scheme (‘Tactical Optimization’) 354 is executed to determine preferred input torques and associated power costs for operating the engine 14 in the all-cylinder state (‘Input Torque Full’), in the cylinder deactivation state (‘Input Torque Deac’), the all-cylinder state with fuel cutoff (‘Input Torque Full FCO’), and in the cylinder deactivation state with fuel cutoff (‘Input Torque Deac FCO’). The system inputs to the tactical optimization scheme 354, as shown in FIG. 4, include the net predicted output torque (‘To Net Prdtd’) and the predicted accelerator output torque (‘To Accel Prdtd’). In operation, the predicted accelerator output torque request (‘Output Torque Request Accel Prdtd’) and the predicted braking output torque request (‘Output Torque Request Brake Prdtd’) are monitored. The predicted output torque requests for acceleration and braking are combined and shaped with the axle torque response type through a predicted output torque shaping filter 352. The net predicted output torque comprises a sum of the operator torque requests communicated through the accelerator pedal 113 and the brake pedal 112. Other inputs include a lead operating range state of the transmission 10 (‘Lead Hybrid Range State’) a lead predicted input acceleration profile (‘Lead Input Acceleration Profile Predicted’), a predicted range of clutch reactive torques (‘Predicted Clutch Reactive Torque Min/Max’) across each applied clutch in the lead operating range state, and predicted battery power limits (‘Predicted Battery Power Limits’).

The lead operating range state of the transmission 10 comprises a time-shifted lead of the operating range state of the transmission 10 to accommodate a response time lag, for example, between the engine torque request and the actual engine torque response. Thus the lead operating range state of the transmission 10 becomes the commanded operating range state. The lead predicted input acceleration profile comprises a time-shifted lead of the desired predicted input acceleration profile of the input member 12 to accommodate the response time lag. Thus the lead predicted input acceleration profile is the predicted input acceleration profile of the input member 12 occurring after the time shift. The parameters designated as ‘lead’ are used to accommodate concurrent transfer of torque through the powertrain converging at the common output member 64 using devices having varying response times. Specifically, the engine 14 can have a response time of an order of magnitude of 300-600 ms, and each of the torque transfer clutches C1 70, C2 62, C3 73, and C4 75 can have response times of an order of magnitude of 150-300 ms, and the first and second electric machines 56 and 72 can have response time of an order of magnitude of 10 ms.

The tactical optimization scheme 354 includes an optimization manager 420 which manages and generates power cost inputs, penalty costs, and optimization inputs for search schemes 402 and 406 and evaluation schemes 404 and 408. The search schemes 402 and 406 and evaluation schemes 404 and 408 determine preferred input torques and corresponding output torques at minimum power costs for operating the powertrain at each of the engine states.

The optimization function 440 of the search schemes 402 and 406 calculates a candidate output torque (‘To(j)’) is based upon the candidate input torque Ti(j). Furthermore, the candidate output torque (‘To(j)’) is limited within a range defined by the predicted accelerator output torque (‘To Accel Prdtd’) and the net predicted output torque (‘To Net Prdtd’), thus limiting the range for the candidate input torque Ti(j).

The search scheme 402 executes a one-dimensional search of the input torque to determine a preferred input torque which minimizes power costs when operating the engine fueled and in the all-cylinder state. At each input torque, a preferred output torque is determined. This includes determining a range of input torques comprising minimum and maximum input torques with the engine 14 operating in the fueled state and in the all-cylinder state (‘Input Torque Minimum Full’, ‘Input Torque Maximum Full’) which are input to a one-dimensional search engine 430. The search engine 430 generates a candidate input torque (‘Ti(j)’) within the range of input torques that is input to an optimization function 440. The optimization function 440 calculates candidate outputs including an output torque (‘To(j)’) that is limited within the range defined by the predicted accelerator output torque (‘To Accel Prdtd’) and the net predicted output torque (‘To Net Prdtd’). Other torque outputs include motor torques for the first and second electric machines 56 and 72 (‘Ta(j)’, ‘Tb(j)’), and output power from the ESD 74 (‘P_(BAT)(j)’), electrical power from the first and second electric machines 56 and 72 (‘Pa(j)’, ‘Pb(j)’) and clutch torque outputs (‘Tcl1(j)’), (‘Tcl2(j)’) of applied clutches of the transmission device 10 based upon the candidate input torque and the optimization inputs and the system inputs. The candidate outputs of the optimization function 440 are input to a cost function 450 which calculates a power cost (‘P_(COST)(j)’)for the candidate input torque. The search engine iteratively generates candidate input torques and executes over the range of input torques to identify a preferred input torque and corresponding output torque which achieves a minimum power cost (‘P_(COST FULL FUEL)’) when operating the engine fueled and in the all-cylinder state.

The search scheme 406 executes a one-dimensional search of the input torque to determine a preferred input torque which minimizes power costs when operating the engine fueled and in the cylinder deactivation state. This includes determining a range of input torques comprising minimum and maximum input torques with the engine 14 operating in the fueled state and in the cylinder deactivation state (‘Input Torque Minimum Deac’, ‘Input Torque Maximum Deac’) which are input to the one-dimensional search engine 430. The search engine 430 generates a candidate input torque (‘Ti(j)’) within the range of input torques that is input to the optimization function 440. The optimization function 440 calculates outputs including an output torque (‘To(j)’) that is limited within the range defined by the predicted accelerator output torque (‘To Accel Prdtd’) and the net predicted output torque (‘To Net Prdtd’). Other torque outputs include motor torques for the first and second electric machines 56 and 72 (‘Ta(j)’, ‘Tb(j)’), and output power from the ESD 74 (‘P_(BAT)(j)’) and electrical power from the first and second electric machines 56 and 72 (‘Pa(j)’, ‘Pb(j)’) based upon the candidate input torque and the optimization inputs and the system input. The outputs of the optimization function 440 are input to the cost function 450 which calculates a power cost (‘P_(COST)(j)’)for the candidate input torque (‘Ti(j)’). The search engine iteratively generates candidate input torques and executes over the range of input torques to identify a preferred input torque and corresponding output torque which achieves a minimum power cost (‘P_(COST DEAC FUEL)’) when operating the engine in the fueled state and in the cylinder deactivation state.

The evaluation scheme 404 evaluates the input torque to determine a preferred output torque and a power cost when operating the engine in the unfueled state and in the all-cylinder state. The candidate input torque (‘Input Torque FCO Full’) is input to the optimization function 440. The optimization function 440 calculates the outputs including an output torque (‘To’) and torque outputs from the first and second electric machines 56 and 72 (‘Ta’, ‘Tb’), and output power from the ESD 74 (‘P_(BAT)’) and power from the first and second electric machines 56 and 72 (‘Pa’, ‘Pb’) based upon the input torque and the optimization inputs and the system inputs. The outputs of the optimization function 440 are input to the cost function 450 which calculates a power cost (‘P_(COST FULL FCO)’) when operating the engine unfueled and in the all-cylinder state.

The evaluation scheme 408 evaluates the input torque to determine a preferred output torque and a power cost when operating the engine in the unfueled state and in the cylinder deactivation state. The candidate input torque (‘Input Torque FCO Deac’) is input to the optimization function 440. The optimization function 440 calculates the outputs including an output torque (‘To’) and torque outputs from the first and second electric machines 56 and 72 (‘Ta’, ‘Tb’), and output power from the ESD 74 (‘P_(BAT)’) and power from the first and second electric machines 56 and 72 (‘Pa’, ‘Pb’) based upon the input torque and the optimization inputs and the system inputs. The outputs of the optimization function 440 are input to the cost function 450 which calculates a power cost (‘P_(COST DEAC FCO)’) for the input torque when operating the engine unfueled and in the cylinder deactivation state.

The optimization function 440 has inputs including a single input torque, the optimization inputs and the system inputs. The system inputs include the net predicted output torque (‘To Net Prdtd’) and the predicted accelerator output torque (‘To Accel Prdtd’). The optimization inputs include the lead operating range state of the transmission 10 (‘Lead Hybrid Range State’) the lead predicted input acceleration profile (‘Lead Input Acceleration Profile Predicted’), the predicted range of clutch reactive torques (‘Predicted Clutch Reactive Torque Min/Max’) across each applied clutch in the lead operating range state, and predicted battery power limits (‘Predicted Battery Power Limits’). Other limits include maximum and minimum motor torque outputs from the first and second electric machines 56 and 72, and system inertias, damping, clutch slippages, and electric/mechanical power conversion efficiencies. For each candidate input torque, the optimization function 440 calculates powertrain system outputs that are responsive to the system inputs comprising the aforementioned output torque commands and are within the maximum and minimum motor torque outputs from the first and second electric machines 56 and 72, and within the available battery power, and within the range of clutch reactive torques from the applied clutches for the present operating range state of the transmission 10, and take into account the system inertias, damping, clutch slippages, and electric/mechanical power conversion efficiencies. The powertrain system outputs include a preferred output torque (‘To’) limited within a range defined by the predicted accelerator output torque (‘To Accel Prdtd’) and the net predicted output torque (‘To Net Prdtd’), and achievable motor torques output from the first and second electric machines 56 and 72 (‘T_(A)’ and ‘T_(B)’).

The cost function 450 determines power costs for operating the powertrain system responsive to the system inputs including the net predicted output torque and the predicted accelerator output torque and with the engine 14 at the candidate input torque. The power costs are determined based upon factors that include mechanical power loss in the form of friction and spin losses, electrical power losses related to heat generation, internal resistances, and current flow, and parasitic losses. During a braking event, the power costs include kinetic power loss due to unrecovered kinetic energy that is expended in the form of heat generation in the friction brakes 94, which can be recovered as electric power through regenerative braking. Costs are assigned and associated with fuel and electrical power consumption and are associated with a specific operating point of the hybrid powertrain. Lower power costs are associated with lower fuel consumption at high conversion efficiencies, lower battery power usage, and lower emissions for each engine speed/load operating point, and take into account the present operating state of the engine 14. The search schemes 402 and 406 include additional power costs comprising engine power costs associated with operating the engine 14 in the all-cylinder fueled state (‘Full Cylinder Engine Power Loss Inputs’) and in the cylinder deactivation fueled state (‘Deac Cylinder Engine Power Loss Inputs’).

A method for operating a hybrid powertrain using a control system is now detailed, with reference to the powertrain system and control system described hereinabove for purposes of illustration. The method is applicable to various powertrain systems that utilize multiple torque generative devices including an internal combustion engine and a second torque machine, and not limited to the system described hereinabove. During ongoing operation, the control system detects a braking event when the operator input to the brake pedal 112 indicates a predicted brake output torque request which has a negative value. The tactical control scheme 330 executes through the tactical optimization control path 350 and the stabilization analysis scheme 356 to determine a preferred engine state and a preferred engine input torque. This includes searching the range of engine input torques for engine operation in the engine states including the all-cylinder state and the cylinder deactivation state, and the engine states including the engine-fueled state and the fuel cutoff state. Preferred output torques that can be reacted through the output member 64 of the transmission 10 to the driveline 90 are determined for each candidate engine input torque along with the corresponding power costs which include kinetic power losses due to friction braking. Output torques that are reactable through the output member 64 of the transmission 10 to the driveline 90 are those that are within the range of the maximum and minimum clutch reactive torques across each of the applied clutches in the lead operating range state and within the battery power limits, and are determined for each of the candidate engine input torques. The preferred engine state and the preferred input torque value are those which minimize the power costs during the braking event. The control system can meet the net immediate output torque request by controlling the powertrain system to react the output torque through the output member 64 to the driveline 90, as executed through the output and motor torque determination scheme 340. This can include immediately operating the engine 14 in the fuel cutoff state to minimize fuel and engine input power to maximize the output power transferred through the transmission 10 which can be reacted through the electric machines and captured as kinetic power which can be transformed to electric power storable in the ESD 74 through regenerative braking.

FIG. 6 graphically shows output torque (‘To’) plotted as a function of input torque (‘Ti’) illustrative of the concept described. Lines depict the input torques comprising the input torque at fuel cutoff (‘Input Torque FCO’) and the minimum and maximum input torques (‘Input Torque Minimum’, ‘Input Torque Maximum’) are shown, along with a maximum output torque (‘To Max’), an optimum or preferred output torque (‘To Opt’) and a minimum output torque (‘To Min’) plotted as a function of input torque Ti and illustrative of one of either the all-cylinder state and the cylinder deactivation state. Exemplary output torque request limits comprising the net predicted output torque (‘To Net Prdtd’) and the predicted accelerator output torque (‘To Accel Prdtd’) are also plotted. Point A depicts input torque from the engine 14 operating at fuel cutoff and the corresponding preferred output torque comprising the net predicted output torque (‘To Net Prdtd’). This demonstrates an operating point whereat the net predicted output torque request can be achieved using reactive torque through the transmission 10. The area between the preferred output torque and the net predicted output torque (shown as area B) represents the output torque comprising the friction braking torque generated at the wheels 93 to produce the net output torque request and thus represents kinetic energy power loss in the form of available and unrecovered brake torque or power loss to the friction brakes 94 through heat. The tactical control scheme 330 can selectively command engine operation in the fuel cutoff state to permit recovery of the brake torque when the minimum and preferred output torques are greater than the net predicted output torque. Specifically, in this operation the engine 14 can be commanded to the fuel cutoff mode and the first and second electric machines 56 and 72 can be controlled to generate motor torques that react with the driveline 90 to achieve the net predicted output torque. The output torque reacted through the first and second electric machines 56 and 72 can be in the form of regenerative power that can be stored in the ESD 74. Thus, during a braking event, the preferred input torque is determined based upon an output torque that is limited within the range defined by the predicted accelerator output torque and the net predicted output torque and minimizes total power costs. The powertrain system operated at an input torque and an output torque responsive to the operator inputs and the system inputs including the net predicted output torque, and is achievable by the powertrain system.

It is understood that modifications are allowable within the scope of the disclosure. The disclosure has been described with specific reference to the preferred embodiments and modifications thereto. Further modifications and alterations may occur to others upon reading and understanding the specification. It is intended to include all such modifications and alterations insofar as they come within the scope of the disclosure. 

The invention claimed is:
 1. Method for controlling a powertrain system including an engine, a transmission and a torque machine connected to an energy storage device, the transmission operative to transfer power between the engine and the torque machine and an output member coupled to a driveline coupled to a wheel including an actuable friction brake, the torque machine operative to react torque transferred from the wheel through the driveline to the output member of the transmission, the engine selectively operative in an all-cylinder state and a cylinder deactivation state and selectively operative in a fueled state and a fuel cutoff state, the method comprising: monitoring operator torque requests comprising operator inputs to a brake pedal and an accelerator pedal; detecting a braking event based upon the operator torque requests; determining a net predicted output torque corresponding to the operator inputs to the brake pedal and the accelerator pedal and determining a predicted accelerator output torque corresponding to the operator input to the accelerator pedal; determining a range of permissible output torques, said range defined by the net predicted output torque and the predicted accelerator output torque, said range further limited based upon a minimum output torque as a function of a minimum input torque; evaluating candidate input torques from the engine for each of the engine states and determining corresponding candidate output torques reactable through the output member of the transmission to the driveline, the candidate output torques limited within the range of permissible output torques; determining power costs for operating the transmission for the candidate input torques; and identifying a preferred engine state and a preferred input torque comprising the candidate input torque and the corresponding engine state having a minimum power cost for operating the transmission during the braking event.
 2. The method of claim 1, comprising determining a preferred output torque within the range of permissible output torques and corresponding to the preferred engine state and the preferred input torque; and controlling the engine based upon the preferred engine state and a preferred input torque and controlling motor torque from the torque machine based upon the preferred output torque.
 3. The method of claim 2, further comprising controlling actuation of the friction brakes based upon the preferred output torque and the operator torque requests.
 4. The method of claim 1, comprising determining the power costs for operating the transmission for the candidate input torques during the braking event based upon unrecovered kinetic energy power loss during the braking event.
 5. The method of claim 1, further comprising executing a search over a range of candidate input torques for the engine in the fueled state and operating in one of the all-cylinder state and the cylinder deactivation state, determining preferred output torques within the range of permissible output torques and reactable through the output member of the transmission to the driveline for the candidate input torques, and determining corresponding power costs for operating the transmission based thereon.
 6. The method of claim 5, further comprising determining candidate input torques for the engine in the fuel cutoff state and operating in one of the all-cylinder state and the cylinder deactivation state, determining preferred output torques within the range of permissible output torques and reactable through the output member of the transmission for the candidate input torques to the driveline, and determining corresponding power costs for operating the transmission based thereon.
 7. The method of claim 1, further comprising iteratively selecting candidate input torques within an allowable range for the input torque, determining a corresponding candidate output torque within the range of permissible output torques and reactable through the output member to the driveline based upon the candidate input torque, determining a friction braking torque based upon the operator torque requests and the candidate output torque, and determining a power cost for operating the powertrain system associated with the operator torque requests; and selecting a preferred input torque comprising the candidate input torque that minimizes the power cost for operating the powertrain system.
 8. Method for controlling a powertrain system including an engine, a transmission and a torque machine connected to an energy storage device, the transmission operative to transfer power between the engine and the torque machine and an output member coupled to a driveline coupled to a wheel including an actuable friction brake, the torque machine operative to react torque transferred from the wheel through the driveline to the output member of the transmission, the method comprising: detecting a braking event based upon operator torque requests comprising operator inputs to a brake pedal and an accelerator pedal; determining a net predicted output torque corresponding to the operator inputs to the brake pedal and the accelerator pedal and determining a predicted accelerator output torque corresponding to the operator input to the accelerator pedal; determining a range of permissible output torques, said range defined by the net predicted output torque and the predicted accelerator output torque said range further limited based upon a minimum output torque as a function of a minimum input torque; evaluating candidate input torques from the engine and determining corresponding candidate output torques limited by the range of permissible output torques and reactable through the output member of the transmission to the driveline; determining corresponding power costs for operating the powertrain to achieve the candidate output torque at the candidate input torque; and identifying a preferred input torque comprising the candidate input torque that minimizes the power costs.
 9. The method of claim 8, further comprising identifying a preferred engine state to minimize the power costs for operating the transmission during the braking event.
 10. The method of claim 8, comprising determining the corresponding power costs for operating the powertrain to achieve the candidate output torque at the candidate input torques during the braking event based upon unrecovered kinetic energy power loss during the braking event.
 11. The method of claim 8, further comprising executing a search over a range of candidate input torque values for the engine in a fueled state and operating in one of an all-cylinder state and a cylinder deactivation state, determining preferred output torques within the range of permissible output torques and reactable through the output member of the transmission to the driveline for the candidate input torque values, and determining corresponding power costs for operating the transmission based thereon.
 12. The method of claim 11, further comprising determining candidate input torque values for the engine in a fuel cutoff state and operating in one of the all-cylinder state and the cylinder deactivation state, determining preferred output torques reactable through the output member of the transmission for the candidate input torques to the driveline, and determining corresponding power costs for operating the transmission based thereon.
 13. The method of claim 8, further comprising iteratively selecting candidate input torques within an allowable range for the input torque, determining a corresponding candidate output torque reactable through the output member to the driveline based upon the candidate input torque, determining a friction braking torque based upon the operator torque requests and the candidate output torque, and determining a power cost for operating the powertrain system associated with the operator torque requests; and selecting a preferred input torque comprising the candidate input torque that minimizes the power cost for operating the powertrain system.
 14. Method for controlling a transmission for a hybrid powertrain system, said transmission operative to transfer power between an input member and a torque machine and an output member, the method comprising: monitoring operator torque requests associated with braking and acceleration; detecting a braking event based upon the operator torque requests; determining a net predicted output torque corresponding to the operator torque requests associated with braking and acceleration and determining a predicted accelerator output torque corresponding to the operator torque request associated with acceleration; determining a range of permissible output torques, said range defined by the net predicted output torque and the predicted accelerator output torque said range further limited based upon a minimum output torque as a function of a minimum input torque; evaluating candidate input torques to the input member and determining corresponding candidate output torques reactable through the output member of the transmission, the candidate output torques limited within the range of permissible output torques; determining power costs for operating the transmission at each of the candidate input torques; and identifying a preferred input torque comprising the candidate input torque having a minimum power cost for operating the transmission during the braking event to achieve the operator torque requests. 